Stepless mechanical torque converter



Aug. 26, 194-1.

P. CICIN v 2,254,195

STEPLESS MECHANICAL TORQUE CONVERTER Filed Aug. 23, 1959 9 Sheets-Sheet 1 7110 5 Toe P1904, c /C// Aug. 26, 1941. P. CICIN STEPLESS MECHANIbAL TORQUE CONVERTER Filed m 23, 1939.

9 Sheets-Sheet 2 Au 26, 1941, P clcm 2,254,195

STEPLESS MECHANICAL TORQUE CONVERTER Filed Aug. 23, 1959 9 Sheets-Sheet 3 Hgn5a' :E: 1 I w I a Aug. 26, 1941. P. CICIN STEPLESS MECHANICAL TORQUE "CON VERTER 9 Sheets-Shed 4 Filed Aug. 23, V 1939 I; Fig.8.

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Au 26, 1941. P I IN 2,254,195

STEPLESS MECHANICAL TORQUE CONVERTER Filed Aug. 23, 1939 9 Sheets-Sheet 5 Aug. 26, 1941. P. CICIN I STEPLESS MECHANICAL TORQUE CONVERTER Filed Aug. 23, 1939 9 Sheets-Sheet 7 Aug. 26, 1941. P c cgN I 2,254,195

STEPLESS MECHANICAL TORQUE FIONVERTER Filed Aug. 2:5, 19:59 9 Sheets-Sheet 8 fivys/v 70 R404 c/cuv Aug. 26, 1941. c am 2,254,195

STEPLESS MEQHANIUAL TQKQUE CONVERTER I Filed Au 2:, 19:59 9 S bsets-Sheet 9 movement and for converting rotating motion of ment of such kind that at any moment the speed UNITED STATES PATENT OFFICE s'rErLEss MECHANICAL 'roaQUE ooNvEn'rEn Paul Cicln, Vienna, Germany Application August 23, 1939, Serial No. 291,602

. In Germany September 5, 1838 7 Claims. (Cl. 74-119) This invention relates to a converter for convertlng torque of rotating motion into linear amplitude as long as the rotating oscillations take place in one direction of rotation only. Since this is not the case at first, as the rotational oscillations are successively in oppositedirections on account of the reciprocating linear oscillations} it is necessary, prior to the combining of the two aforesaid rotational movements or oscillations, to rectify them, i. e. to convert them to a single unchanging direction of rotation. When this is attained, the two parts performing the rotating oscillations have always the same direction of rotation and their instantaneous speeds are at any moment positive and proportional to the sin or cos of the polar or turning angle of the driving rotation. I

The required rectification of the rotating oscillationsv is attained, according to the invention, by a double planetary reversing gear for each. The essential feature of this reversing gear is that all gear teeth remain always engaged and one speed into rotating motion of another speed.

Essentially, two groups of mechanical torque 5 or revolution converters of rotating motion, ad Justable without steps, are known, of which one utilizes friction, whereas to the other one belong the so-called barring gears, where a uniform driving rotation is converted into adjustable oscil- 1 latory or reciprocating movements, from which, by means of freewheel ratchets, a drive-off rotation is produced. The former type of gear lends itself only to the transmission of small quantities of power, whereas the so-called barring gears while capable of transmitting greater power are of limited applicability also. Besides, there is one fundamental deficiency in the barring gears, inasmuch as the freewheel ratchet gear transmits to the drive-ofi shaft not a uniform drive-off moment, but rotational force impulses which are converted into a practically uniform rotation only by the fly-wheel effect of the driven masses.

The invention set forth below consists in the provision of a stepless mechanical torque or revolution converter, by which the uniform driving rotation will be converted, without shocks and without recourse to compensating flywheel masses, into an identically uniform drive-off rotation with any number of revolutions whatever, both theoretically and practically without lossavoiding the usual frictional losses in bearlugs and gear wheels.

The invention provides the following procedure to attain this end: The driving rotation is first 3 converted into two turning -motions and then each of these into a linear reciprocating movedouble gear, due to the automatic locking of one of its members takes place for a definite direction of rotation, whereas the other part runs during that stage of operation. Now, this locking must be realisable in any position desired, actuable by the strokes, adjustable as desired, of the linear oscillations, and this only in one direction, whereas rotation in the other direction must take place at a high mechanical efiiciency. This locking, according to the intent of the present invention, is so accomplished that to either half of each of the two reversing gears there is connected a device consisting of two worm wheels with their worms, one worm of which has so small an angle of inclination of the thread as to be self-locking of the part linearly reciprocating to and fro will, respectively, neglecting the direction as represented by the sign, be proportional to the sin or cos of the respective angle of the uniform driving rotation movement. Furthermore it will be possible to impart a variable amplitude to the linear reciprocating movements, from a maximum value down to zero. The linear reciprocating movements of this variable amplitude are then converted into rotating oscillations that likewise obey the sin or cos law as far as speed is concerned, and it is obvious that these rotating movements or oscillations, in accordance with the goniometric formula: K. sin a+K. QOS a=K (K being a value depending on the oscillation ampli locking worm, thu b i prevent d f tude, or the polar angle of rotation about the axis turning, whereas, on the other hand, no-load of the driving shaft), can be converted into uni- 55 action becomes operative when, with the opposite the other worm has as great an angle of inclination of the thread as possible for the. purpose of obtaining a high efficiency. The teeth of the one side only, that is in the opposite directions of rotation, and have, in the other direction, an essential side play so that with one direction of rotation one worm enters into action and with the other direction of rotation the other worm enters into action. The two worms are interconnected by a gear. The locking action is accomplished in such a way that in the respective direction of rotation one worm wheel bears against the selfform rotation corresponding to the selected that the coming into operation of one part of the light and transmits no torque and thus no powerin all circumstances, whereas, on the other hand,

worm wheels are in contact with the worms at direction of rotation, the second worm wheel actuates the non-self-locking worm and, through the aforesaid gear, actuates also the self-locking worm. The rotational oscillations thus rectified and, as to their speed, proportional to the sin or cos of the polar angle of rotation about the axes of the driving shaft, are now united in a common differential gear in such a way that a uniform rotation will be derived from it. In con nection with the conversion of the uniform driving rotation into a sin and cos linear reciprocating movement of adjustable amplitude it is further pointed out that, according to the course of the time-speed curves, both the acceleration and retardation process have a very favorable development and therefore permit of high speeds of revolution being attained, without excessive inertia forces or even shocks occurring.

Figures 1 to 17 show two practical of the invention.

Fig. 1 shows the device, by which the uniform driving rotation is converted into linear reciprocating movements. Figs. 3 and 4 represent how the amplitude of the original movement changes; Fig. 3-A is a transverse section taken on line AA of Fig. 3; Fig. 2 shows the con-.- version of these linear movements into rotational oscillations. In Figures 5 to 11, one of the rectifiers to have both rotations in the same direction is shown both in its general arrangement and in its details, whereas in Figs. 12 and 13 examples 'the differential gear which effects the combination of the two rotational oscillations into a uniform drive-off rotation, is represented. Fig. 14 shows the general arrangement of the converter. Finally, Figs. 15, 16 and 17 show another practical embodiment of the invention, by means of which the linear oscillations performed at a speed proportional to the sin or cos of the angle of rotation of the driving shaft, are produced. Figs. 15 and 16, in particular, show the details of the design, whereas Fig. 17 represents the general arrangement for resolving the rotating motion into the two partial oscillations. Fig. 15A is a transverse section taken on line 3-3 of Fig. 15. V 3

Referring to the figures'in detail, Fig. 1 shows the two cam discs 3 and 4 operated, with a uniform number of revolutions, by the driving shafts I and 2; the shape of cams 3 and 4 is determined from the condition that the push rod I, which is guided in a straight line and which, through the rollers 5 and 8, is in constant contact with the two cam discs, performs linear displacements, or reciprocating movements, whereas the instantaneous speed of rod 1 must always be proportional to the square of the sine of the turning or polar angle a of shafts l and 2 with reference to a fixed radius of origin, that is, v=2lc sin l a (i. e. change the right side of the equation to 2k sin a). The time-path curve, i. e. the law of motion is, consequently, found here by integration of the speed-time equation to be R==lc ai-lc sin a cos n+1, where k signifies a constant; the minus applies to the sin, the plus to the cos oscillation and r is the radius of roller 6. When tracing out, measuring from the circumference of an assumed base circle 8 drawn about the axis of shaft 2 as center, and proceeding to either side of the radius of origin or initial direction 0'-O, the radius vectors R. thus found, corresponding to the respective traversed time or position of turning or polar angle of rotation between 0 and 180, measured by the corresponding radii passing through the radius of rollers 5 and 5, in which circles the end points of the radii are shown as centers. If radius vector R is measured from the axis of shaft 2 as a pole, the constant r should be changed to r-i-s, where s is the radius of base circle 8. As can be seen from Fig. 1, the shapes are identical for both the cam discs 3 and 4 which also occupy the same positions on the shafts l and 2. A simple reflection shows that the two other cam discs not shown in the drawings, which are to determine the speed of the other push rod in accordance with a cos law, have also the identical shape, with the only difierence of being displaced 90 in relation to the sin cam discs. Push rod 1 is guided in its reciprocating linear motion by bearings 8 and In.

The linear reciprocating movements thus produced are, at first, of the same value in amplitude. For the transformation of this amplitude there serves the device represented lnFigs. 2, 3

and 4. From Fig. 3 it can be seen that the linear motion of push rod 1, by means of bolt ii, is transmitted to the rocking arm 13 pivoting round the pivot I2, which forces thisarm also to make osciliatory movements, of the same kind, around the pivot It. At its other end, the rocking arm i3 is connected, through a pivot bolt H, with another push rod :5 which is guided in a straight line and which therefore, in its turn, performs linear reciprocations, though of an amplitude different from that of push rod 1'. However, since the pivot I! of rocking arm I3 is adjustable along a guide rail IS, the amplitude of the movements of push rod l5 can be altered to any extent and continuously. Since the center line of guide rail'l'fi forms two similar triangles with the center line of rocking arm l3 and with the center lines of the two push rods! and IS, the motion law derived from the shape of the cam discs remains intact also with the altered amplitude. The rocking arm I3 is provided, on the side of the pivot bolt II, with a longitudinal slot, since, owing to being guided in straight lines, the distance apart of the two bolts II and I4 varies during motion. Bolt I2 is adjusted by the adapting piece I! guided in rail l8, by turning the screw ll. As can be seen from Fig. 14, the screws for the two pairs of com disks are coupled to one another. standstill of push rod Ii occurs with continued reciprocating movement of push rod 1, whenby shifting of the adapting piece I! the axes of the two pivot bolts i2 and I4 are brought to coincidence; moreover, by shifting the fulcrum or pivot bolt l2 it is possible to create movements of larger and smaller amplitude than performed by the push rod I. The two halves of the pivot bolt [2 are connected by the stirrup I! which signed as not to affect the coincidence of bolts I2 and I4. The linear motion of push rod II is accomplished by the guide bearings 20 and 2!. Outside these bearings, push rod II is, on one side. provided with a toothed rack 22, with which the spur wheel 24, turning upon the shaft 13, engages, see Fig. 2. The spur wheel 24 thus takes care of the linear movements of push rod II, converting them into rotational oscillations.

The speed of the rotational oscillations thus obtained will, at any time, be proportional to the sin or cos of the polar angle of rotation being combined into a uniform rotation. .This' task is accomplished by the rectifier represented in Figs. to 11. It consists, as mentioned above, I

of a double planetary gear of such design that the torque will always be transmitted from one half, whereas the other runs light. Accordingly, two sun wheels 25 and 2b are shrunk on shaft 23, Fig. 5, upon the circumference of whichthere runs a planetary wheel pair for each. The planetary wheels 27, 2t pertaining to the sun wheel 25 engage with the teeth 29 of the wheel 3b and are supported, through the spindles ti and 82, on the wheel disc 33 rotatably mounted upon the shaft 23. In a similar manner the two planet Wheels 36, 35 of the sun wheel 26 engage with the I teeth as of the wheel 3% which has internal teeth,

whereas their spindles ti and 9d are supported in the wheel it. The wheel 36 is fastened upon the shaft 39 which turns in the hearings to and ti and is independent of shaft 23. The wheel 3t carries, in addition to its internal teeth 29, external teeth 42, by means of which it operates the spur wheel M shrunk on the shaft 53.

The rectifying effect is accomplished in the following manner: In one direction of rotation of shaft 23 it is the wheel disc 83 that is held in-place, whereas the wheel dd turns freely without resistance, while on reversal of the direction the gearing 5t, 62, so that notwithstanding the diflerent angles of pitch'or inclination the two worms drive their worm wheels at the same angular speed. For the same reason ore worm has been designed left-handed and the other right-handed. Besides, in the self-locking worm Sfi-E'ig. 8only the right-hand faces of the teeth bear against the corresponding left-hand faces of teeth 48, whereas, on the other hand, the steep pitch worm 49, which is not self-locking (Fig. 9), bears only with ,the left-hand faces of its teeth against the corresponding right-hand faces of teeth 66, while the opposite faces have in the ,two cases a considerable play: ti and $2 respectively.

The action is such that whe torque is applied which tends to rotate wheel at in one sense, through the teeth 48 of the worm wheel M, a pressure is exerted on the tooth faces of the self-locking worm 50, and the wheel M and thus also the wheel ,86 are prevented from turning, whereas with the torque applied in the opposite sense the tooth faces 56 of wheel 35 exert a of rotation of shaft 23 the wheel as is prevented from turning, whereas the wheel disc 33 turns freely. By this means, at one moment the pair of axles 3!, 32 of the planet wheels 2?, 28 are held fast and the planet wheels enabled to transmit the torque and thus the power to the internal teeth 29 of wheel 36 and the next momentfdue to the engaging internal teeth it of wheel 36', the transmission of the torque to wheel 30 through the spindles 371, as of the planet wheels 38, is again made possible. As can be seen from Figs. 10 and 11, with alternating direction of rotation of shaft 23 there results an unchanging direction of rotation of wheel 39 and thus also of spur wheel ie and shaft 63;. Besides, in Figs. 5, 10 and 11, the proportions in size of the internal wheels 25, 2d and of the planet wheel pairs 21, 2t and as, do, are so selected that in the two directions of rotation the speed development for wheel 3d is the same. Furthermore, it can easily be seen from the figures that the reactions of spindles El, 32 on the wheel disc 33 on the one hand and of the planet wheels 3%, 35 on the internal teeth $5 on the other hand, with unchanging direction of rotation of wheel 36, are always rectified so that wheel disc 83 and wheel 36 will offer resistance in one direction only when transmitting the torque.

This operating characteristic is made use of in the devised arrangement of the lpcking device. This will be clear by reference to Fig. 5 and Figures 6, 7, 8 and 9, which refer to the righthand locking device of Fig. 5. Fig. 5 shows that -wheel 36 has been designed as a worm wheel with teeth 46 and that on the same shaft 39 which carries wheel 36, another worm wheel 41 with'teeth 48 is shrunk on. With each of the worm wheels a worm, which is the steep-pitch,

not self-locking worm 49 (here shown as quadpressure on the steep-pitch worm d5, put it in motion, and operate, through the gearing 5!, 52, also the self-locking worm 58 which, in consequence, looses its self-locking action for this direction of rotation.

When, by shifting the aforementioned pivot bolt lZ-Fig. 3so as to coincidewith the pivot bolt it, the no-load position is reached, the opposite rotation of shaft 35, i. e. the reverse run,

can be efiected by displacing the worms in their axial directions, but in opposite directions. This can be accomplished by shifting the bearing I26 of worm 50, Fig. 6, to the left. as=far as the dotted position through the spindle I21, and by simultaneously shifting the bearing I28 to the right,

position shown dotted in Fig. 7, through the spindle I29. By means of a safety device it can 33 provided with the worm gear teeth 53 is connected to the second worm wheel "55 by means of a hollow shaft 56 in which the shaft 23 freely turns. With teeth 56 of worm wheel 55 there engages the self-locking worm 51, theshaft of which, by means of the spur gearing E8, 59, is

connected to the shaft of the steep-pitch worm 6d engaging with the worm wheel 33. Since both for one direction of rotation and the other direction, one tooth face of a worm wheel is always sin function, since the values always remain positive. A similar rotation, but with a displacement of phases corresponding tothe course of the cos function, is transmitted by the shaft 63 starting from the second gear half-see Fig. 14-

so that the two can be combined to a-uniform rotational motion, but of a number of revolutions K. sin a+K. cos=a==K.

This adding of the two rotating motions takes place in the planet gear shown in Figs. 12 and 13, consisting of the sun wheel 64 shrunk on shaft 43, of the two planet wheels 65, 66 running on its periphery with the spindles 51, 68 and the wheel 69, with the internal teeth of which engage the planet wheels. This wheel is, in addition, provided with external teeth II, with which engages the spur wheel 12 fitted on shaft 63. The spindles 61, 68 of the planet wheels 65, 60 are firmly carried on a double support I4 the drive-off shaft 13. I In order that the combination of the two rotating motions in the revolving gear should produce a uniform rotation of the drive-oif-shait 13, the spur wheel 12 inserted between wheel 69 and shaft 63 must bring about a slowing down in the rotation of wheel 69 in relation to the angular speed of shafts l3 and 63; this retarding factor is always smaller than unity, and, as follows from one of the known calculation methods, equal to the relation between the number of teeth of sun wheel 84 and thenumber of teeth of the internal toothing 10 of wheel 69. Since only one wheel is required for producing this gear ratio, the locking gear of the second gear half must be so adjusted that shaft 53 has always a direction of rotation contrary to that of shaft 03.

The uniform rotation thus obtained of the drive-off shaft 13 does not require any compensation by a fly wheel, .or by fly wheel mass, etc. The

uniformity of the drive-ofl is conditioned only by the uniformity of the drive.

Fig. 14 shows a general assembled arrangeshrunk on ment of the whole system and also the connection of the two shaft pairs I, 2 and 15, 10 of the curve disc or cam pairs 3, 4 and I1, I0 through the connecting shaft I9 and their drive by the main drive shaft 80. Fig. 14 represents, in addition, the connection of spindle II, which alters the oscillation amplitudes and thus the number of revolutions, to the correspondingspindle CI of the other gear half through shaft 82, on whichlatter the hand wheel 83 is shrunk. By turning this hand wheel, the pivots I2 and 88 of the rocking arms I3 and 85 respectively. are shifted by means of the spindles, the amplitudes of the reciprocating linear movements of the push rods I5 and 81 altered, and thus finally the number of revolutions of the drive-ofl regulatedas may be desired. In this figure, the first push-rod of the second gear half is marked with 80 and the shaft to the second planet gear with".

Figures 15, 16 and 17 represent a second embodiment of the invention, by means of which i the uniform driving rotation is converted into linear reciprocating movements of varying amplitude developing according to the speed law: K. 8111 11 and K. C0520: respectively. In place of the curve discs or cams of the first example there .are two pairs of cone-shaped bodies uniformly operated, the cross sections of which, perpendicular to the axis of rotation, are so designed that they cause the respective linear guided push rod situated each between a pair of conical bodies and in permanent contact with these two pairs to make .reciproc'ating linear movements of the eating linear motion of the desired amplitude by displacing the pair of conical bodies inrelation vto the push rod, and thus the desired number .sectional curves drawn in.

In correspondence are the sectional curves: QI-M; 92-95 and 93-98; the motion of the 'push rod along the sectional curves 93-96 corresponds to the maximum amplitude, whereas the push rod is stopped and no-load operation begins, as soon as the push'rod 91 and the rollers 98, 89 pivoting at its end are in contact with the pair of sectional curves SI-Sl. For the conical bodies there are employed, in' addition, the generating lines of 22 30' as being 22 '30 and it should here be pointed out, especially with regard to manufacture, that these generating lines are straight. The conical bodies can be shifted on their driving shafts I00 and IN respectively. For the transmission of the torque between driving axle and conical body, the shafts I00 and IOI are flattened at one side and the guides in the conical bodies fitted to-the cross sections of the shafts. The conical bodies are shifted by'the frame I02. Fig. l5-A shows a sectional view of the linear guide I02 of push rod 01 taken on line B-B of Fig. 15. From these two figures can be seen also the toothed rack I04 of push rod 81, by means of which the linear reciprocating movements are converted into rotational oscillations of the spur wheel I06 fastened on the shaft I05.

Fig. 16 shows the pair of conical bodies with guide frame, push-rod etc. in plan. Finally, Fig. 17 shows an assembled arrangement of the two pairs of conicalbodies 89, 90 and I01, I08, and of their common guiding by the frame I02, since the displacement of the two pairs must take place at the same time and always to the same extent. The frame I02 slides between the external guide rails I00 and H0 and the intermediate rail III. The frame is shifted by spindle II2 which engages with suitable threads of the frame and is operated by the hand wheel I II. In this ease also, the two pairs of driving shafts I00, IN and Ill, iii, are connected by shaft H0 operated from the main shaft III. Shaft I00 mentioned above and the corresponding shaft H9, actuated by push rod N0, of the other gear half, operate, through the gearings I20, I2I and I22, I22, respectively. the shafts I24 and I25 respectively, which correspond to the shafts 23and 88 of Fig. 14.

While in the second example one-pair of conical bodies is required to control each push rod, only two cams or curve discs could, of

specified kind' and of a definite amplitude.

Owing to the fact that to every-cross section corresponds a definite amplitude and that the cross sections without discontinuity passinto one another, the push rod can begiven the reciprocourse, do as well in the first example, if these are provided with grooved guides of the specified shape. Likewise, in place of the described rectifler, especially for the transmission of small torques, a free-wheel ratchet or a different rectifier mightbe used. Also in place of the curve discs or conical bodies a different device answering the same purpose can be employed.

Having now particularly described and seer.- tained the nature of my said invention, and in what manner the same is to be performed, I declare that what I claim is:

1. Ina stepless mechanical torque converter for converting original uniform rotary motion of a given speed into consequent uniform rotary motion of a different speed, a rotary drive element carrying said original uniform rotary motion, linear converting means comprising a pair tion, linear converting means comprising a pair of units connected for and adapted to convert said original rotary motion of said rotary drive element into two independent-linear reciprocating movements whose instantaneous linear speeds are respectively proportional to the sine square and cosine square of the polar angle of rotation of said rotary drive element relative to a fixed reference radius about the axis of said rotary drive element, means for varying the amplitudes of each of said linear movements, and

terminal rotatable means connected and adapted 3: A converter according to claim 1, said linear converting means comprising a pair of conical bodies whose surfaces are shaped to produce said'sine and cosine relation of tlie instantaneous speeds of the-polar angle of rotation of said rotary drive element.

4. A converter according to claiml, said terof units connected for and adaptedto convert said original rotary motion of said rotary drive element into twoindependent linear reciprocating movements, means for varying the amplitudes of each of said linear movements, and

- terminal rotatable means connected and-'adapted for converting and combining said linear movements to produce resultant uniform rotating movement of desired'speed each of said units comprising a cam the contour of whose periphery is the curve represented in polar coordinates with 'the axis of said rotary drive element as a pole by the equation R kaik Silla COSa-I-T, where R is the radius vector and a is the angle between 'the radius vector and a fixed reference origin radius, and r and k areconstants, and the plus sign before the second term refers toone of said units and the minus sign refers to the other of said units.

6. A converter according to claim 1, said amplitude varying means comprising .a pair of linear displaceable elements connected by lever means whose fulcrum is selectively adjustable for varying the amplitude of the resultant linear movements of oneof said elements with reference to the amplitude of the applied linear movements I of the other of said elements.

minal means comprising controllable planetary.

gears connected for converting both of said linear movements into two rotating movements both rotating in the same sense.

5. In a stepless mechanical torque converter for converting original uniform rotary motion of a given speed into consequent uniform rotary motion of a different speed, a rotary drive element carrying said original uniform rotary mo- 7. A converter according to claim 1, said terminal means comprising controllablecooperating planetary gears and cooperating worm 'wheels and worms, one of said worms having relatively fiat teeth of pitch substantially perpendicular to the axis of said worm and being self-locking, and.

another of said worms having teeth oblique to the axis of said worm and not being self-locking.

PAUL CICIN. 

